CN109072983B - Shaft-hub connection structure - Google Patents

Shaft-hub connection structure Download PDF

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Publication number
CN109072983B
CN109072983B CN201680079447.XA CN201680079447A CN109072983B CN 109072983 B CN109072983 B CN 109072983B CN 201680079447 A CN201680079447 A CN 201680079447A CN 109072983 B CN109072983 B CN 109072983B
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China
Prior art keywords
shaft
section
hub connection
hub
turbine
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Active
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CN201680079447.XA
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Chinese (zh)
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CN109072983A (en
Inventor
G·戴默
S·德尔哈尔特
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/007—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid combination of cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/20—Mounting rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F16D1/068—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving gluing, welding or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/32—Application in turbines in gas turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/60—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/36—Retaining components in desired mutual position by a form fit connection, e.g. by interlocking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

A shaft-hub connection (1), in particular for mounting a rotor wheel on a shaft (10). The shaft-hub connection (1) comprises a shaft (10), a hub (20) and a filling material (30). The shaft (10) has an end section (11) at one end. A receiving region (21) is arranged in the hub (20). The end section (11) is arranged in the receiving region (21) with the filling material (30) as an intermediate layer. The filling material (30) forms a snap-fit in the axial direction and in the rotational direction relative to the end section (11) and relative to the receiving region (21), so that the shaft-hub connection (1) is formed in a form-fitting manner.

Description

Shaft-hub connection structure
Technical Field
The invention relates to a shaft-hub connection, in particular for connecting a rotor wheel to a shaft.
Background
Shaft-hub connection structures are known in various embodiments from the prior art, for example from the textbook "Roloff/Matek Maschinenelement: Normung, Berechung, Gestalturn" (Vieweg + Teubner Verlag, German and Western documents.
The known shaft-hub connection does not integrate the properties of small installation space, high force and torque transmission, and high strength. For example, a spline connection, although having a high torque transmission, is not suitable for transmitting axial forces; for this purpose, an additional axial safeguard must be provided, which in turn requires additional installation space.
Disclosure of Invention
The shaft-hub connection according to the invention, however, has a high force and torque transmission and high strength while having only a small overall size.
To this end, the shaft-hub connection includes a shaft, a hub, and a filler material. The shaft has an end section at one end. A receiving area is arranged in the hub. The end section is arranged in the receiving region with the filling material as an intermediate layer. The filling material forms a snap (Hinterschnitte) in the axial direction and in the rotational direction relative to the end section and relative to the receiving region, so that the shaft-hub connection is embodied in a form-fitting manner.
By means of the form-locking engagement, extremely high forces and torques can be transmitted without the strength being adversely affected by the pretensioning. Furthermore, the connection is arranged in a mounting space-saving manner in the receiving region of the hub; thereby eliminating additional mechanical parts, such as screws. Preferably, the clamping of the shaft-hub connection is carried out without play, so that the force and torque transmission takes place without losses and without shocks. Thereby also maximizing the efficiency and life of the shaft-hub connection.
The shaft-hub connection according to the invention is particularly suitable for mounting a rotor wheel on a shaft, wherein the rotor wheel forms the hub. Since the shaft-hub connection is arranged in the interior of the rotor wheel, the flow geometry of the rotor wheel is not influenced by the shaft-hub connection.
In an advantageous embodiment, the end section has a positioning section. The filling material forms a rotational snap fit with the structure formed on the positioning section. The rotary clamp is used for transmitting extremely high torque. Preferably, the structure is configured such that the structure has a small notch effect to secure high strength of the shaft-hub connection structure.
Advantageously, the structure is configured as a groove in the axial direction. Preferably, a plurality of grooves are arranged distributed over the circumference. This results in a particularly high and uniform torque transmission.
In an advantageous embodiment, the end section has a connecting section adjacent to the positioning section. The filling material forms an axial snap-fit with the transition from the positioning section to the connecting section. Extremely high axial forces can be transmitted by this axial clamping. Preferably, the transition from the positioning section to the connecting section is configured such that it has a small notch effect to ensure a high strength of the shaft-hub connection.
The rotary as well as the axial clamping is very advantageously arranged in the interior of the hub or rotor wheel. The shaft-hub connection is thus implemented in a very space-saving manner; without adversely affecting the outer geometry of the shaft and in particular also of the hub as a result of other connecting techniques, for example screw connections.
In an advantageous embodiment, the receiving region has a positioning region, wherein the filling material forms a further rotational latching with the geometry formed on the positioning region. The additional rotary latch serves to transmit extremely high torques. Preferably, the geometry is configured such that it has a small notch effect to ensure a high strength of the shaft-hub connection.
Advantageously, the geometry is designed as a through-groove in the axial direction. Preferably, a plurality of through-grooves are arranged distributed over the circumference. This results in a particularly high and uniform torque transmission.
In an advantageous embodiment, the positioning region is arranged to enclose the positioning section externally. Thereby optimizing torque transfer between the shaft and the hub; disadvantageous twisting of the filling material is thus prevented.
In an advantageous embodiment, the outer diameter D of the positioning section11aAnd the inner diameter D of the positioning area21aAs large. The positioning section thereby interacts with the positioning region in the radial direction, so that a coaxial orientation of the shaft relative to the hub is achieved.
Advantageously, at least one latching surface is formed on the positioning region. The filling material forms an axial clamping with the at least one clamping surface. Optionally, a plurality of bayonet surfaces may be provided. The axial snap-in action is such that: the axial snap-fit prevents the filler material from being withdrawn from the hub; i.e. the clamping surface points into the interior of the receiving region.
In an advantageous embodiment, the end section has a connecting section adjacent to the positioning section and a pressing section that engages onto the connecting section. At least one axial surface is formed on the pressing section. The filling material forms a further axial snap-fit with the at least one axial face. Alternatively, a plurality of axial faces may be provided. The additional axial snap-fit action: which prevents the shaft from being withdrawn from the filler material; i.e. the axial face is directed out of the receiving area.
In an advantageous embodiment, the end flank formed on the hub interacts with a shoulder formed on the shaft in the axial direction of the shaft. This forms an axial stop of the shaft on the hub during assembly of the shaft-hub connection, so that the shaft can be positioned in an axially defined manner relative to the hub. Axial tolerances of the shaft-hub connection can thereby be minimized.
Advantageously, the filling material is made of a casting material that hardens by itself or under the influence of temperature. The process of establishing the shaft-hub connection is thus very simple to carry out.
Preferably, the filler is made of an adhesive or an elastomer. Thereby, the shaft-hub connection structure has good damping characteristics and thus can well damp impact loads.
In a further embodiment according to the invention, the shaft-hub connection is used in a turbine. The turbine here comprises a rotor wheel arranged on a shaft. The rotor wheel is arranged on the shaft by means of the aforementioned shaft-hub connection. The rotor wheel here forms the hub of the shaft-hub connection. The compact design of the shaft-hub connection also makes it possible to make the rotor wheel very small without adversely affecting the flow geometry of the rotor wheel.
In an advantageous embodiment, the turbine is arranged in a waste heat recovery system of an internal combustion engine. The waste heat recovery system has a circuit for guiding a working medium. The circuit comprises, in the flow direction of the working medium, a pump, an evaporator, a bypass valve, an expander and a condenser. The expander is implemented as a turbine having a shaft-hub connection according to the present invention. For this application, the operating state of the turbine and thus the rotational speed of the rotor wheel often change. A seamless implementation of the shaft-hub connection is particularly suitable for this. Furthermore, particularly as an application in the automotive field, a small structural size of the waste heat recovery system and of the turbine is required, for which the above-described embodiments of the shaft-hub connection are particularly suitable.
In a further advantageous embodiment, the turbine is arranged in a heat pump. The heat pump includes a condenser, an evaporator, and a turbine, wherein a rotor wheel of the turbine functions as a compressor between the evaporator and the condenser. The shaft-hub connection according to the invention is particularly suitable for use in heat pumps due to the small overall dimensions and the capability of transmitting high torques.
In a further advantageous embodiment, the turbine is arranged in a micro gas turbine, wherein a rotor wheel of the turbine serves as a compressor for a turbine rotor of the micro gas turbine. With a small overall size and the ability to transmit high torques, a turbine having a shaft-hub connection according to the invention is particularly suitable as a compressor for a micro gas turbine.
Alternatively, the rotor wheel can also function as a turbine rotor wheel of a micro gas turbine.
In a further advantageous embodiment, the turbine is arranged in an internal combustion engine, wherein a rotor wheel of the turbine acts as an additional compressor for compressing combustion air which is supplied to the internal combustion engine. The requirements for such rotor wheels are small overall dimensions, the ability to transmit high torques and high strength. The shaft-hub connection according to the invention is therefore particularly suitable as a connection technique for shafts and rotor wheels.
Drawings
Fig. 1 shows the components of the shaft-hub connection before assembly, wherein only the main regions are shown.
Fig. 2 schematically shows the shaft-hub connection in the assembled state.
Fig. 3 shows the shaft-hub connection according to the invention in the assembled state, with the hub hidden.
Fig. 4 shows a further embodiment of the shaft-hub connection according to the invention in the assembled state, in which the hub is concealed.
Fig. 5 shows a longitudinal section through the filling material of the shaft-hub connection in a further embodiment.
Fig. 6 schematically illustrates a waste heat recovery system.
Fig. 7 schematically shows a heat pump.
Fig. 8 schematically illustrates a micro gas turbine.
FIG. 9 schematically illustrates another micro gas turbine.
Fig. 10 schematically shows an internal combustion engine with an additional compressor.
Detailed Description
Fig. 1 shows a shaft 10, a hub 20 of a rotor wheel and a filling material 30, which are joined in the assembled state to form a shaft-hub connection 1. Fig. 1 shows the two components, shaft 10 and hub 20, and filling material 30 in this case before they are joined to form the shaft-hub connection 1. According to the invention, the filling material 30 is strongly deformed or plasticized during the joining process of the shaft-hub connection 1, so that a form-locking connection is formed. Extremely high forces and torques can thereby be transmitted, for example, higher than in the case of conventional press-fit connections or toothed or wedge connections.
In the embodiment of fig. 1, the filling material 30 is strongly deformed during the joining of the shaft-hub connection 1, optionally with strong heating of the filling material 30. For this purpose, the filling material 30 can also be of annular design or of hollow-cylindrical design, for example. The shaft 10 has a three-part end section 11, wherein the end section 11 is reduced in diameter relative to a middle region 19 of the shaft 10. The hub 20 has a receiving area 21 in the form of an approximately arbitrarily complex slot. In the exemplary embodiment of fig. 1, the receiving region 21 is embodied in two parts.
The end section 11 is the region of the shaft 10 which, in the assembled state of the shaft-hub connection 1, interacts with the receiving region 21 of the hub 20, optionally with the filler material 30 as an intermediate layer, in order to transmit forces and torques.
The inner geometry of the hub 20, i.e. the geometry of the receiving region 21, and the outer geometry of the end section 11 of the shaft 10 have a radial as well as an axial geometry:
the receiving area 21 has a positioning area 21a and a clamping area 21 b. The end section 11 has, from the inside outwards, a positioning section 11a, a connecting section 11b and a pressing section 11 c. The connecting section 11b and the pressing section 11c are regions of the shaft 10 which are arranged in the snap-in region 21b in the assembled final state of the shaft-hub connection 1. The positioning portion 11a interacts with the positioning region 21a in a form-fitting manner, advantageously with the filler material 30 as an intermediate layer, such that a relative rotation and a relative movement of the shaft 10 relative to the hub 20 are prevented.
In order to position the shaft 10 axially relative to the hub 20, a pair of stop surfaces is formed on the shaft 10 and the hub 20, wherein two alternatives exist:
the end flank 22 formed on the hub 20 interacts with the shoulder 12 formed on the shaft 10 in the axial direction of the shaft 10. The shoulder 12 is here the end flank at the transition from the end section 11 to the middle region 19 of the shaft 10.
The hole bottom 23 formed in the receiving region 21 interacts with the cover surface 13 formed on the pressing section 11 c. The cover surface 13 is here the end side of the pressing section 11c and thus the outermost end side of the shaft 10.
The pair of stop surfaces, i.e. end side surface 22/shoulder 12 or bore bottom 23/cover surface 13, axially position the shaft 10 relative to the hub 20 upon contact during assembly. The stop surfaces shoulder 12 and end flank 22 are preferably used here, since they do not press against one another with the filling material 30 as an intermediate layer.
When engaging the shaft-hub connection 1, the filling material 30 is first compressed by the end section 11 such that it is arranged annularly around the connection section 11b and the compression section 11c, i.e. approximately axially clamped between the positioning section 11a and the compression section 11 c. See also fig. 3.
Preferably, however, the filling material 30 fills the entire gap between the end section 11 and the receiving region 21, i.e. between the positioning section 11a and the positioning region 21 a. See also fig. 2. For this purpose, the end section 11 also preferably has a cylindrical ring section 11d between the positioning section 11a and the intermediate section 19, which ring section prevents the filling material 30 from being drilled out of the gap between the end section 11 and the receiving region 21.
In the embodiment of FIG. 1The bit section 11a and the compression section 11c are spline-shaped and the connection section 11b is cylindrical. It is advantageous here if the diameter D of the connecting section 11b11bSmaller than the outer diameter D of the positioning section 11a11aAnd is also smaller than the outer diameter D of the pressing section 11c11c(ii) a Thereby creating an axial snap-fit of the shaft 10 relative to the filler material 30.
Advantageously, the compression section 11c and the connection section 11a have the same geometry in cross section to minimize manufacturing costs. The geometry of the pressing section 11c is selected here such that it can be pushed past the positioning region 21a during assembly. Preferably, the gap between the pressing section 11c and the clamping region 21b is kept as small as possible, so that too much filler material 30 does not have to be filled into the gap, since the gap is secondary to the function of the shaft-hub connection 1 in certain embodiments, in particular without large axial forces. Fig. 4 shows an example with a cylindrical compression section 11 c.
In the embodiment of fig. 1, the positioning section 11a is preferably spline-shaped in configuration, with grooves 11a1 to anchor the filler material 30 in these grooves 11a 1; thereby completing the rotational snap-fit. Alternatively, the pressing section 11c may also have such a groove 11c1 as shown in fig. 1. Furthermore, the positioning region 21a has a through-opening 21a1, which is likewise used for anchoring the filling material or for additional rotational latching.
In the embodiment of fig. 1, clamping region 21b is cylindrically embodied with diameter D21bWherein D is21bGreater than the inner diameter D of the positioning area 21a21a(ii) a This results in a clamping of the filling material 30 relative to the hub 20 at the transition from the clamping region 21b to the positioning region 21 a.
The snap fit of the filler material 30 relative to the shaft 10 and relative to the hub 20 coacts such that the filler material 30 prevents the shaft 10 from being withdrawn from the hub 20. The shaft-hub connection 1 is thus only detachable when the filling material 30 is melted again.
The torque transmission between the shaft 10 and the hub 20 or the rotor wheel 20 takes place primarily via the positioning section 11a, the filling material 30 and the positioning region 21 a. The filling material is anchored in the slot 11a1 of the shaft 10 and the through slot 21a1 of the hub 20 and thus forms a form-lock in the direction of rotation with respect to the shaft 10 and the hub 20. In the embodiment of fig. 1, the number of the grooves 11a1 and the through grooves 21a1 may be different from each other.
Outer diameter D of positioning section 11a11aAdvantageously not greater than the inner diameter D of the positioning zone 21a21a. Particularly preferably, D11aAnd D21aAre equally large so that the outer diameter D11aAnd an inner diameter D21aCoacting such that they cause a coaxial orientation of the hub 20 relative to the shaft 10, also as shown in fig. 5.
For this purpose, outer surfaces 11a2 are formed on the positioning section 11a, more precisely on the teeth between the grooves 11a1, which outer surfaces together form the diameter D11aHas a cylindrical surface with a hollow portion. Analogously, inner surfaces 21a2 are formed on the positioning region 21a, more precisely on the teeth between the through-grooves 21a1, which inner surfaces together form the diameter D21aHas a cylindrical surface with a hollow portion. Within the scope of manufacturing tolerances, in this embodiment, for coaxial positioning of the shaft 10 and the hub 20, D11a＝D21a. Preferably, the number of the outer surfaces 11a2 and the inner surfaces 21a2 is equal here.
In a development of the embodiment of fig. 1, the positioning section 11a and the positioning region 21a can also be configured such that they form a spline connection, if appropriate with the filling material 30 as an intermediate layer. The positioning region 21a has a negative concave shape of the positioning section 11a in the case of manufacturing and fitting tolerances. Accordingly, in these embodiments, the outer diameter D of the positioning section 11a11aGreater than the inner diameter D of the positioning area 21a21a。
Advantageously, the shaft 10 is clamped with the hub 20 via the filling material 30 without axial play. The axial force flow acts via an axial clamping of the pair of stop surfaces, i.e. end flank 22/shoulder 12 or hole bottom 23/cover surface 13, and filling material 30 relative to receiving region 21 and end section 11: for this purpose, axial faces 11a3, 11c3, advantageously the end faces of grooves 11a1, 11c1, are formed on the pressing section 11c and optionally on the positioning section 11 a. Furthermore, an axial surface is likewise formed on the positioning region 21a as a latching surface 21a3, advantageously as an end surface of the through- groove 21a 1.
A plurality of catches are thus formed in the axial direction:
axial clamping between the filling material 30 and the clamping surface 21a3 of the positioning region 21 a. This axial snap-fit prevents the filler material 30 from being withdrawn from the hub 20.
Optional axial snap-fit between the filling material 30 and the axial face 11a3 of the positioning section 11 a.
Additional axial snap-fit between the filling material 30 and the axial face 11c3 of the pressing section 11 c. This additional axial snap-fit prevents the shaft 10 from being withdrawn from the filler material 30.
The dimensioning of the snap-in region 21b, the connecting section 11b, the pressing section 11c, the positioning region 21a, the positioning section 11a and the filling material 30 must be coordinated with one another in order to achieve a high degree of filling after the shaft-hub connection 1 has been assembled. The filling material 30 can be, for example, a metal which melts during assembly by heating (for example by induction) and is pressed into the clamping region 21b by engaging the shaft 10 into the hub 20.
However, the filling material 30 may alternatively be a two-component adhesive, which is filled in the liquid state and then, during assembly, is distributed into the detent regions 21b and, if appropriate, into the positioning regions 21a and subsequently hardens. Preferably, the hardening takes place autonomously in this case. Other materials, such as elastomers or different particles, may also be used as the filler material 30. If an elastomer is used as the filling material 30, the shaft-hub connection structure 1 has a high degree of damping. If particles are used as the filler material 30, a heat treatment of the assembled shaft-hub connection 1 is carried out if necessary in order to bring the filler material 30 to its final strength.
It is expedient for the mounting direction of the shaft 10 to be directed from above into the receiving region 21, so that the filling material 30 does not flow out of the receiving region 21 due to gravity. Air which is to be forced out of the interspace between the end section 11 and the receiving region 21 during assembly can escape through the correspondingly configured channel. The filler material 30 must be designed for specific environmental conditions, in particular for thermo-mechanical loads.
Fig. 2 shows the shaft-hub connection 1 in the assembled or engaged state. The filling material 30 has reached its final configuration and fills the gap between the receiving area 21 and the end section 11. The filling material 30 is arranged here to surround the connecting section 11b, so that clamping with respect to the shaft 10 and the hub 20 takes place, which clamping effects a form-fitting connection in the axial direction. However, the filling material 30 also surrounds the positioning section 11a and the pressing section 11 c.
In this way, in one embodiment, the filler 30 fills the gap region between the positioning section 11a and the positioning region 21a, and torque transmission is performed without a gap via the spline connection between the positioning section 11a and the positioning region 21 a.
In another embodiment, the filling material 30 fills the groove 11a1 and the through groove 21a1, so that the filling material 30 produces a form-locking in the direction of rotation between the shaft 10 and the hub 20, wherein the form-locking is also free of gaps.
In both embodiments, the shaft-hub connection 1 is thus embodied very rigidly. Furthermore, the screw connection between the shaft 10 and the hub 20 is thus eliminated. If the hub 20 is designed as a rotor wheel 20 of a turbine, the wheel projections 29 of the rotor wheel 20, which are arranged axially opposite the receiving region, can be configured in a flow-technically optimized manner, without the screw connection having to be considered here.
Fig. 3 shows the shaft-hub connection 1 according to the invention in the assembled state, wherein the hub 20 or the rotor wheel 20 is concealed. The filling material 30 is arranged annularly around the connecting section 11b of the shaft 10. This produces an axial form-fit with respect to the geometry of the positioning region 21a of the concealed hub 20.
In most embodiments of the shaft-hub connection 1, the filling material 30 is also arranged to annularly surround the pressing section 11c and optionally also the positioning section 11 a. But this is not shown in the present fig. 3 for display reasons.
Fig. 4 shows a further exemplary embodiment of a shaft-hub connection 1 according to the invention in the assembled state, wherein the hub 20 is concealed. In contrast to the embodiment of fig. 3, the pressing section 11c is embodied cylindrically and the filling material 30 is arranged to partially surround the positioning section 11 a.
Figure 5 in clamping orThe longitudinal section of the filling material is shown in the assembled state. In this embodiment, the outer diameter D of the positioning section 11a11aAnd the inner diameter D of the positioning region 21a21aAre equal in size. Thus, the inner surface 21a2 of the positioning region 21a co-acts with the outer surface 11a2 of the positioning section 11a and orients the hub 20 coaxially with the shaft 10.
Fig. 6 shows a waste heat recovery system 100. The waste heat recovery system 100 has a circuit 100a guiding the working medium, which circuit comprises, in the flow direction of the working medium, a pump 102, an evaporator 103, a bypass valve 104a, an expander 104 and a condenser 105. Collection container 101 is attached to circuit 100a via valve assembly 101 a; alternatively, the collecting container can also be inserted into the circuit 100 a.
The liquid working medium is conveyed by the pump 102 from the circuit 100a or from the collecting container 101 into the evaporator 103, where it is evaporated by the thermal energy of the exhaust gas of the internal combustion engine. The evaporated working medium is then relieved of pressure in the expansion machine, while outputting mechanical energy, for example to a generator or a transmission, not shown. The working medium is then liquefied again in the condenser 105 and conducted back into the collecting container 101.
Optionally, a bypass passage 106 is disposed alongside the expander 104. Depending on the operating state of the internal combustion engine and the parameters resulting therefrom, for example the temperature of the working medium, the working medium is supplied to the expander 104 via the bypass valve 104a or is bypassed from the expander via the bypass channel 106. For example, a temperature sensor 107 is arranged before the condenser 105. The temperature sensor 107 determines the temperature of the working medium upstream of the condenser 105 and supplies a corresponding signal to a control unit, not shown. The control unit actuates the bypass valve 104a as a function of various data, for example the temperature of the working medium upstream of the condenser 105.
According to the invention, the expansion machine 104 is designed as a turbine and comprises a rotor wheel 20 which is fastened to the shaft 10 by means of a shaft-hub connection 1, wherein the shaft 10 acts in this embodiment as a driven shaft.
Fig. 7 schematically shows the use of the shaft-hub connection 1 according to the invention in a turbine 75 of a heat pump 70, wherein the turbine 75 operates as a compressor. The heat pump 70 has a working medium circuit 77 with a condenser 71, an evaporator 72, a throttle valve 73 or expansion valve and a turbine 75.
The evaporator 72 evaporates the previously liquid working medium, which is then compressed by the rotor wheel 20 of the turbine 75 and supplied to the condenser 71. In the case of the output of thermal energy, for example into the thermal system of a house, the working medium is liquefied again in the condenser 71. The working medium is then relieved in a throttle 73 or via an expansion valve and supplied to the evaporator 72 again.
According to the invention, the rotor wheel 20 of the turbine 75 is fastened on the shaft 10 by means of the above-described shaft-hub connection 1, wherein, in this embodiment, the shaft 10 acts as a drive shaft.
Fig. 8 schematically shows the use of the shaft-hub connection 1 according to the invention in a turbine 89, wherein the turbine 89 operates as a compressor. The micro gas turbine 80 has a turbine runner 81 and a turbine 89. The turbine runner 81 is arranged on the shaft 10 as is the rotor wheel 20 of the turbine 89. The combustion air 85 is compressed in the turbine 89 and supplied to the combustion chamber 82 of the micro gas turbine 80.
The combustion air 85 is mixed with fuel 86 in the combustion chamber 82 and ignited, thereby driving the turbine rotor 81. Forming high temperature and pressure-relieved exhaust gases 87. The exhaust gases 87 can then be cooled in a heat exchanger, not shown, and the combustion air 85 can be preheated at the same time. The turbine runner 81 drives the shaft 10 and thereby also the rotor wheel 20 of the turbine 89 via this shaft.
According to the invention, the rotor wheel 20 and/or the turbine rotor wheel 81 of the turbine 89 are fastened on the shaft 10 by means of the shaft-hub connection 1 described above.
Fig. 9 schematically shows another application of the shaft-hub connection 1 according to the invention in a turbine 91. The micro gas turbine 90 has a turbine 91 with a rotor wheel 20, a compressor impeller 93, and a combustion chamber 92.
The rotor wheel 20 of the turbine 91 is optionally arranged on the shaft 10 in the same way as the compressor impeller 93. The combustion air 95 is compressed in the compressor by the compressor rotor 93 and supplied to the combustion chamber 92 of the micro gas turbine 90. Combustion air 95 is mixed with fuel 96 in combustion chamber 92 and ignited, thereby driving rotor wheel 20 of turbine 91. Forming high temperature and pressure-relieved exhaust 97. The rotor wheel of the turbine 91 drives the shaft 10, whereby the compressor impeller 93 is in turn driven.
According to the invention, the rotor wheel 20 of the turbine 91 and/or the compressor impeller 93 are fastened on the shaft 41 by means of the shaft-hub connection 1 described above.
Fig. 10 schematically shows an arrangement of a turbine 62 with a rotor wheel 20 as an additional compressor for an internal combustion engine 61.
Combustion air 65 is supplied to turbine 62 via an intake duct 66 and is compressed there by rotor wheel 20. The compressed combustion air 65 is supplied to the internal combustion engine 61 via a pressure line 67. After the combustion process in the internal combustion engine 61, the exhaust gases are conducted away via an exhaust system 68. The high temperature exhaust gases in the exhaust train 68 may also be used in other embodiments to preheat the combustion air in the intake pipe 66.
According to the invention, the rotor wheel 20 of the turbine 62 is fastened to the shaft 10 or drive shaft by means of the shaft-hub connection 1 described above.
The shaft-hub connection 1 according to the invention works as follows:
the filler material 30 creates a snap-fit between the shaft 10 and the hub 20 both circumferentially and axially. Advantageously, these catches are seamless, so that forces and moments can be efficiently transmitted between the shaft 10 and the hub 20.
The shaft-hub connection 1 is particularly suitable for smaller constructions, such as for example small turbines 62, 75, 89, 91, wherein the rotor wheels 20 of the turbines 62, 75, 89, 91 are fastened to the respective shaft 10 by means of the shaft-hub connection 1.
In particular, when the overall size of the rotor wheel 20 is small, it is virtually impossible to provide a screw connection to the shaft 10 due to the lack of installation space. Furthermore, the flow-favorable configuration of the wheel projection 29 brings about great advantages, even in the case of small structural dimensions, which cannot be achieved optimally owing to the screw connection.
In the specific case of applications in which rotor wheels 20 must be mounted on both ends of shaft 10, additional problems arise in the assembly of second rotor wheel 20: the complex formed by the shaft 10 and the first rotor wheel 20 needs to be fixed in order to produce a screw connection by means of a corresponding pretensioning force or tightening torque. The fixed retention of the first rotor wheel 20 is hardly possible or extremely disadvantageous because of the fine structure, since this can lead to a change in the shape of the rotor wheel 20 or to damage. The geometry of the rotor wheel 20 is very unsuitable for the clamping for assembly, in particular when the structural dimensions are small.
The shaft-hub connection 1 according to the invention, however, displaces the connection of the rotor wheel 20 to the shaft 10 into the hub 20 or rotor wheel 20. In this case, the additional material (e.g., metal with a lower melting point, potting compound, adhesive, elastomer), i.e., the filler material 30, is melted or filled in liquid form, for example, by an external heat source and is pressed into the corresponding recess by engaging the end section 11 of the shaft 10 into the hub 20, so that a radially and axially positive connection between the end section 11 of the shaft 10 and the receiving region 21 of the hub 20 is formed.
In the case of melting of the filling material 30, it then solidifies again; the other filler material 30, such as an elastomer or different particles, is brought to its final strength or final shape by a heat treatment after the joining process, if necessary after a chemical reaction.
The resulting shaft-hub connection 1 has the advantages that:
a simultaneous form-locking between the shaft 10 and the hub 20 in radial and axial direction,
a cost-effective connection is provided for,
high precision in the radial and axial positioning of the shaft 10 with respect to the hub 20,
significantly reduced installation space relative to conventional connection techniques,
the wheel inlet geometry or the wheel projection 29 can be optimally configured with regard to flow guidance,
depending on the application, a large selection of possible filling materials 30,
even other functions, such as damping, can be achieved by the specific filling material 30.

Claims (18)

1. A shaft-hub connection (1), wherein the shaft-hub connection (1) comprises a shaft (10), a hub (20) and a filler material (30), wherein the shaft (10) comprises an end section (11) at an end, wherein a receiving region (21) is arranged in the hub (20), which receiving region (21) is closed except for an opening for receiving the shaft (10), wherein the end section (11) is arranged in the receiving region (21) with the filler material (30) as an intermediate layer, wherein the filler material (30) forms a snap connection in the axial direction and in the rotational direction relative to the end section (11) and relative to the receiving region (21) such that the shaft-hub connection (1) is embodied in a form-locking manner, characterized in that,
the end section (11) has a positioning section (11a), a connecting section (11b) and a pressing section (11c) from the inside to the outside,
the receiving area (21) has a positioning area (21a) and a clamping area (21b) from outside to inside,
the positioning region (21a) interacts with the positioning section (11a), the connecting section (11b) and the pressing section (11c) interact with the latching region (21b),
an outer diameter D of the positioning section (11a) up to the outer surface11aAnd the inner diameter D of the positioning area (21a) to the inner surface21aThe size of the air duct is the same as the size of the air duct,
the diameter D of the connecting section (11b)11bIs smaller than the outer diameter D of the pressing section (11c)11cThe outer diameter D of the pressing section (11c)11cIs smaller than the diameter D of the clamping area (21b)21b。
2. The shaft-hub connection (1) according to claim 1, characterized in that the filling material (30) forms a rotational snap with a structure configured on the positioning section (11 a).
3. A shaft-hub connection (1) according to claim 2, characterized in that the filling material (30) forms a further rotational snap with a geometry configured on the positioning region (21 a).
4. A shaft-hub connection (1) according to claim 3, characterized in that the positioning region (21a) is arranged to externally enclose the positioning section (11 a).
5. Shaft-hub connection (1) according to one of claims 1 to 4, characterized in that at least one latching surface (21a3) is formed on the positioning region (21a), wherein the filling material (30) forms an axial latching with the at least one latching surface (21a 3).
6. The shaft-hub connection (1) according to claim 5, wherein the end section (11) has a connecting section (11b) adjacent to the positioning section (11a) and a pressing section (11c) engaging thereto, wherein at least one axial face (11c3) is formed on the pressing section (11c), wherein the filling material (30) forms a further axial engagement with the at least one axial face (11c 3).
7. A shaft-hub connection (1) according to one of claims 1 to 4, characterized in that an end flank (22) configured on the hub (20) co-acts with a shoulder (12) configured on the shaft (10) in the axial direction of the shaft (10).
8. A shaft-hub connection (1) according to one of claims 1 to 4, characterized in that the filling material (30) comprises a castable material.
9. A shaft-hub connection (1) according to one of claims 1 to 4, characterized in that the shaft-hub connection (1) is used for fitting a rotor wheel on a shaft (10).
10. A shaft-hub connection (1) according to claim 2, characterized in that the structure is configured as an axial groove (11a 1).
11. A shaft-hub connection (1) according to claim 3, characterized in that the geometry is configured as a through groove (21a1) in axial direction.
12. A shaft-hub connection (1) according to claim 8, characterized in that the castable material is self-hardening.
13. A turbine (62, 75, 89, 91) with a rotor wheel (20) arranged on a shaft (10), characterized in that the rotor wheel (20) is arranged on the shaft (10) by means of a shaft-hub connection (1) according to one of claims 1 to 12.
14. Waste heat recovery system (100) having a circuit (100a) guiding a working medium, wherein the circuit (100a) comprises, in the flow direction of the working medium, a pump (102), an evaporator (103), a bypass valve, an expander (104) and a condenser (105), wherein the expander (104) is configured as a turbine according to claim 13.
15. A heat pump (70) having a condenser (71), an evaporator (72) and a turbine (75) according to claim 13, wherein the rotor wheel (20) acts as a compressor between the evaporator and the condenser.
16. A micro gas turbine (80) having a turbine (89) according to claim 13, wherein the rotor wheel (20) acts as a compressor for a turbine rotor wheel of the micro gas turbine.
17. A micro gas turbine (90) having a turbine (91) according to claim 13, wherein the rotor wheel acts as a turbine runner wheel of the micro gas turbine (90).
18. An internal combustion engine (61) having a turbine according to claim 13, wherein the rotor wheel (20) acts as an additional compressor for compressing combustion air (65) supplied to the internal combustion engine (61).
CN201680079447.XA 2016-01-19 2016-12-22 Shaft-hub connection structure Active CN109072983B (en)

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DE102016200628.2A DE102016200628A1 (en) 2016-01-19 2016-01-19 Shaft-hub-connection
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US11428158B2 (en) 2022-08-30
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CN109072983A (en) 2018-12-21
US20200386153A1 (en) 2020-12-10

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